Signature flatwise gathering machine



Dec. 9, w52 P. E. KL'EINEBERG ETAL 2,521,039

SIGNATURE FLATWISE GATHERING MACHINE Filed June 28, 1947 T111- yf 12 Sheets-Sheet l BY Moa/wam, Km

Dec. 9, w52 P. E. KLEINEBERG ETAL 2,621,039

SIGNATURE FLATwIsE GATHERING MACHINE Filed June 28, 1947 12 Sheets-Sheet 2 Dec. 9, 1952 P. E. KLEINEBERG ErAL .2,621,039

SIGNATURE FLATWISE GATHERING MACHINE Filed June 28, 1947 TETE' e f INVENTORS; ,0.5. Ha/5526- /0- 4e/10525.

BY 311mm, Kw 4MM/ ATTO R N EYS Dec. 9, 1952 Y P. E. KLEINEBERG ETAL 2,621,039

SIGNATURE FLATwIsE GATHERING MACHINE Filed June 28, 1947 12 Sheets-Sheet 4 INVENTORS; f0.5 MEM/5526 A2/WEEE, BY www ATTORNEYS.

Dec. 9, 1952 P. E. KLElNx-:BERG ETAL 2,621,039

sxGNATuRE FLATwIsE GATHERING MACHINE l2 Sheets-Sheet 5 Filed June 28, 1947 4 Z4 07 5 OVW, M www 7 i. v .U g (l1 ,6 uw .nM/H M o M M U, Il @illu im mm E i n [rl :I IUMII o @A l 3 h T M/ G o M l M 56 \P. 5 M n OBE E T55 C N N R Ewr O VE@ T m7 wf 5P. m K im mmm,

Dec. 9, 1952 P. E. KLEINE-BERG ETAL 2,621,039

SIGNATURE FLATwIsE GATHERING MACHINE Filed June 28, 1947 12 Sheets-Sheet 6 ail;

ATTORNEYS.

Dec. 9, 1952 4P. E. KLEINEBl-:RG r-:TAL

SIGNATURE FLATwIsE GATHERING MACHINE 12 Sheets-Sheet 7 Filed June 28, 1947 3. Mw. u :E E Lr S52 5 REE Y O N W E ma( .MM EAg O 5 VK 5 2 NZ n Z 5 1E A 7.

mmm) Kw 12 Sheets-Sheet 8 P. E. KLEINEBERG ETAL SIGNATURE FLATWISE GATHERING MACHINE 12 Sheets-Sheet 9 P. E. KLEINBERG ET A L lSIGNATURE FLATWISE GATHERING MACHINE w@ Q@ QN o Dec. 9, "1952 Filed June 28, 1947 o Illlllllll Dec. 9, 1952 P. E.K| E1NEBERG ETAL. 2,621,039

SIGNATURE FLATWISE GATHERINC MACHINE l2 Sheets-Sheet lO Filed June 28, 1947 y sa@ www d m w L m N T O O .IE W A l l, w., l mm. mwN ---i l EN n 4 m QR v n- 1, IV .Il l f, h HH- www A ri h /mwm www Em 11| n E.

Dec. 9, 1952 P. E. KLEINEBERG ETAL -SIGNAI'URE FLATWISE GATHERING MACHINE l2 Sheets-Sheet Il Filed June 28, lS-x/ Dec 9, 1952 P. E. KLEINEBERG ETAL SIGNATURE FLATwIsE GATHERING MACHINE Filed June r28, 1947 12 Sheets-Sheet 12 www@ INVENTORS E /E/NE 0YP E. BY WM Kw- ATTORNEYS,

Patented Dec. 9, 1952 UNI ED STATES TENT OFFICE SIGNATURE FLATWISE GATHERING MACHINE Paul E. Klcineberg, Easton, Pa.,

and Pierre New York Application .lune 28, 1947, Serial No. 757,846

(Cl. 27d-54) 19 Cairns. l

This invention is an improved signature flatwise gathering machine, that is, a machine adapted for the extraction of signatures, which term includes single sheets, from a succession of stacks thereof and their discharge unopened to a continuously advancing conveyor, upon which the successive signatures become grouped atwise and travel along through the length of the machine, as the groups accumulate, and therebeyond are delivered for further operations, such as attaching or stapling together the signatures of each group, so as to constitute a book or magazine, and in some cases applying covers thereto. Such kind of gatherer is distinguished from an insert or saddle gatherer wherein the signatures are opened en route and assembled astride a traveling saddle conveyor.

A general object of the present invention is to afford a iiatwise gathering machine of exceedingly high speed of operation and increased rate of output of signature groups, involving the coordination of the several component mechanisms of the machine to give the desired high speed without introducing operative drawbacks. To carry out this important purpose, the operations of extraction of successive signatures from each of the stacks and the transfer and discharge thereof to the conveyor are herein performed by a rotary means, preferably in the conventional form of a continuously rotated drum carrying grippers to grip the signatures for extraction and to release them for discharge.

Further objects include relative simplicity of structure and action, along with compactness of mechanism; the several coordinated component mechanisms being specically improved to afford a faster rate of output than with heretofore known flatwise gathering machines.

Other objects and advantages will be pointed. out in the hereinafter following description of an illustrative embodiment of the invention or will be understood by those conversant with the subject. To the attainment of such objects and advantages the present invention consists in the novel flatwise gathering machine and the novel features of combination, operation, arrangement and structure herein illustrated or described.

The nearest known prior art consists of the machine shown in the following mentioned U. S. patent illustrating certain general principles of flatwise gathering which are utilized also in the machine of the present invention, which latter embodies also various additional features available for use upon the machine of said prior patent, and in some cases adapted also for use otherwie. Kleineberg Patent No. 2,020,321, of November 12, 1935, shows an automatic gathering machine wherein a longitudinal row or series of hoppers carry stacks of signatures each resting flatwise upon a hopper floor which is considerably inclined laterally, with the lowermost signature exposed underneath at its leading edge or margin, and combined therewith the following operating mechanisms; a suction detaching device mounted to swing bodily inward below the stack and out again to clear the stack and, while inward, to swing up and down to and from the exposed margin or a leading corner of the lowest signature, thus to engage and deect the same downwardly from the stack; also a rotary kind of separating means for the leading edge of each signature, adapted to enter between the detached signature edge and the stack above and operating by a wedging action to depress or deflect downwardly the signature edge, while exerting lifting pressure upon a part of the stack, to relieve excessive friction and facilitate the extraction of such signature; also an extractor drum beneath each hopper, continuously rotated, and carrying grippers to grin the detached and depressed leading edge of the lowest signature, thereby to pull the signature from the stack in the extracting direction, the drum carrying or transferring the signature thence downwardly and around for release and discharge advancingly beneath the drum: and an endless conveyor longitudinally traveling with continuous advance beneath the row of stack hoppers, and conventionally shown as a chain with pusher pins, acting upon the received signatures, the pins and the signature groups partaking of the advancing travel to the nal delivery point of the conveyor. Said patent shows also a calipering device or gage to rietect errors in or absence of signatures during their transfer from hopper to conveyor: the same utilizing a signature gripping jaw of the drum for detecting purposes and functioning through a trip device partly carried on the drum to display a visual signal and to stop the machine for correction of the error.

The known prior machines failed to attain in full the desired advantages mentioned, and others; for example, the operating speed of certain of the mechanisms was handicapped by deciencies in others because of practical incapability of the latter to operate at high enough speeds, such as are of the greatest industrial importance. Taking an instance, and assuming a rate of the order of cycles per minute, the complete cooperative actions of the signature detacher mechanism and of the means for separating the leading edge of each lowermost signature from the stack above, in preparation for its extraction, must be performed within a time of onehalf second; and moreover these actions must overlap in that while each lowermost signature is still being separated away from the stack above, for extraction purposes, the detacher must be caused to enter in between such signature and the remaining stack above and commence its detaching action upon the next succeeding signature, thus to condense and abridge the cycle and avoid a delay which may be relatively substantial in prolonging the cycle and may therefore proportionately require more machines and oor space to turn out a given edition, as of a popular magazine. Similar considerations and others pertain to the action of extracting from the hopper each detached and separated signature and drawing it away by the drum in time to permit the actions at the hoppei` to be repeated on schedule. The actions at the drum discharge, and the conveying along of the accumulating groups, must keep pace promptly and reliably with the above operations; while superior handling of the grouped signatures during advancing conveyance is conducive to optimum quantity and quality of product; as is also a durably reliable detection and elimination of defective signatures and groups. The present invention is believed to meet these desiderata in a manner to constitute a salient advance in the gathering department of the book or pamphlet manufacturing art.

By way of preliminary outline, and to establish terminology, the machine of this invention may be described as comprising, in addition to the long and heavy frame parts and base, the power and drive means and other general parts, the following mechanical element-groups or mechanisms constructed, arranged and interconnected for cooperative action upon the series of stacks of signatures, one stack per section, these stacks and their hoppers constituting the infeed positions of the machine, and to manipulate these supplies of signatures to convert them into a procession of flatwise gathered groups accumulated and finally delivered singly at the outfeed position of the machine, namely:

A. The elevated stack hopper in each section of the machine, providing a longitudinal series of stacks, more or less in number according to the number of signatures to be grouped in each nal product; each hopper supporting its signatures flatwise, with the foremost or lowermost thereof exposed underneath at its leading edge to be pulled out longitudinally from the bottom of the stack in what may be termed the extracting direction, generally the opposite to the direction of travel of the conveyor below.

B. The suction detacher means, operating at the leading edge or corner of the lowest or bottom signature in each stack, this, on conventional lines, initiating the extraction operations for each of the successive signatures.

C. The signature separator means, operating next in order upon the signature, preparing for the extraction and comprising primarily a depressor to deflect and hold downwardly the detached signature edge.

D. The stack lifter means, as a secondary part of each separator means, this, like the depresser, reaching into the space between the detached signature and the stack above, the lifter operat- CFI 4 relieve the weight thereof sufficiently to insure the safe and reliable extracting of the signature.

E. The extractor means or rotary drum mechanism, having one or more sets of peripheral grippers and timed to grip each bottom signature in each hopper and draw it out from the stack in the aforesaid extracting direction generally.

F. The group conveyor or endless chain, having signature receiving or pushing means, traveling advancingly beneath the series of extractors and hoppers, thereby receiving in each conveyor pocket or space a complete series or set of signatures forming a group for final delivery.

G. The jogging means, operating alongside and in conjunction with the endless conveyor to align the successive groups following the reception of the successive signatures, thus to insure final alignment of each completed group in readiness for immediately following binding thereof.

H. The detecting means, operable in each section upon each signature, during its passage between hopper and conveyor, with caliper to gage the absence of a signature or a defect in the thickness thereof, being thereby adapted to afford any desired correction or control, such as the stoppage of the machine, together with showing a signal to indicate the location of the defect.

In the accompanying drawings is shown an illustrative embodiment of the invention wherein, on Sheet 1, Fig. 1 is a general lefthand elevation, partly broken away in vertical section through one of the drum shafts; and Fig. 2 is a similar elevation of a detail of Fig. 1.

On Sheet 2, Fig. 3 is a top plan view of Fig. 4 showing the signature hopper and associated suction detacher, the rear side of the hopper being nearest to the observer; and Fig. 4 is a rear elevation thereof.

On Sheet 3, Fig. 5 is a lefthand elevation of the hopper; and Fig. 6 is a perspective view of a typical signature with explanatory legends.

On Sheet 4, Fig. 7 is a top plan view of Fig. S showing the separator means, including the signature depresser and stack lifter and their operating mechanisms, the rear parts thereof being nearest to the observer; and Fig. 9 is a rear elevation thereof.

On Sheet 5, Fig. 9 is a lefthand elevation of the separator mechanism, seen as in Fig. 1, but on a larger scale and detached as a unit from the machine; and Fig. 10 is a top plan view of certain parts thereof, partly in section on the line lll-ID of Fig. 8.

On Sheet d, Fig. 11 is a front elevation of the detector means including the calipering mechanism and certain nearby parts; Fig. 12 is a similar view of the gaging members and parts irnmediately actuated through them, showing positions thereof different from Fig. 11; while Fig. 12 is an exploded view of a detail thereof.

On Sheet 7, Fig. 13 is a partial top plan view of Fig. 14, which latter is a lefthand elevation of the detector mechanism including the parts shown in Figs. 11 to 13 and certain additional parts; and Fig. 15 is a top plan view of a detail thereof.

On Sheet 8, Fig. 16 is a lefthand elevation of the drum, which, like Fig. 1, is partly broken awa,7 in vertical section through one of the drum shafts, showing details of the drum; Fig. 1'7 is a front elevation thereof partly broken away; and Fig. 17' is a similar partial view of a detail.

On Sheet 9, Fig. 18 is a top plan view showingr certain general parts of the machine, and certain other parts including the driving connecing to uplift partially the stack above so as to 7g tOIlS for the everal extracting drums, the rear side of the machine being nearest to the observer; and Fig. 19 is a rear elevation thereof, showing certain additional parts; the drawing being based on the system of constructing the machine in structural units of four gathering sections per unit, as indicated in Figs. 18 and 19 by the dotted line extensions of the bed, the cam shaft and parts above.

On Sheet 10, Fig. 20 is a partial front elevation of the combined lower lefthand and righthand ends of the machine, the middle being largely omitted to condense the figure, and showing particularly the endless conveyor and jogger belts or chains and the drive mechanisms therefor.

On Sheet 11, Fig. 21 is a top plan View of the parts shown in Figs. 20, 23 and 24; and Fig. 22 is an enlarged front elevation of the side-by-side conveyor and jogger chains and their upstanding pins, with dotted line indication of relative jogging or pulsating movements of the latter.

On Sheet l2, Fig. 23 is a righthand elevation of the drive mechanisms for the conveyor and jogger chains shown in Figs. 20 and 21, together with various nearby parts, taken partly in section on the line 23-23 of Fig. 20; and Fig. 24 on an enlarged scale is a front elevation of certain details of said drive mechanism, shown partly in section n the line Z-Z of Fig. 23.

In Various gures signatures S are shown stacked and in process of corner detachment by suction, followed by edge separation, and then extraction, discharge and accumulation into groups. A signature may be considered as composed of various numbers of sheets, as low as two or even one, but usually a considerably larger number, produced by the folding and refolding of a large printed sheet. A conventional signature S is pictured in Fig. 6, having a closed back edge S', to be later bound with the other signatures of each group, as by staples, located for example as indicated. What is known as the signature head S2 is preferably the trailing end or edge, the signature being extracted by its foot end or leading edge S3. At the fourth side is the open front edge S4.

After the separation and extraction of each signature by its leading edge S3 it is transferred around and down for discharge to the conveyor, so that the conveyed signatures, and the groups thereof, are by this invention pushed advancingly by their trailing head ends S2, while their back side edges travel or slide along upon the conveyor trough or raceway in contact with a gaging shoulder or wall; so that the back edges S and the head ends S2 become the gaging or aligning edges for the accumulating signatures in each group, logged into position in each conveyor section as will be described, and thus affording uniormity of assembled condition of the successive groups emerging from the final delivery.

For the purpose of suction-detaching and separation downwardly of each signature leading end below the stack, the operations are commenced at the triangular area or .corner S5, which is the left-rear portion as the signature lies in the hopper, adjacent to the leading edge S3 and back edge S; these operations, lpreparatory to extraction, involving Ia down-swinging by suction of the corner area S5 about a convenient diagonal bend line S6, preferably extending at an angle of 45 to the signature edges and bounding the corner S5, followed by a depressing of the leading edge into the reach of the extractor'. The bend line of the signature corner may be substantially 'at the axis of the sucker swing.

Terms of position or direction, such as front and back, left and right, herein used for facility 'of description, are not intended as limitations. In Fig. 1 the righthand side of the figure is considered the front, whereat the attendant can best observe the signatures and operations; so that Fig. 1 is a lefthand view, partly in section. Like- Wise, the longitudinal conveyor is designated -as traveling rightwise as seen from the front, wherefore the extraction direction is generally the opposite, o-r leftwise from the stack, although obviously the entire design might be reversed.

Taking Fig. 1 as the main drawing, this sh-ows at least some of the parts of each of the component mechanisms hereinabove designated as A to H inclusive. Thus in addition to the sectional bedplate 3l and other xed or frame parts to be described, Fig. 1 shows at the top the hopper or stack mechanism marked A, containing supplies of signatures S; the hopper -being more fully shown in Figs. 3 to 5. A minor portion of the suction detaching mechanism seen in Fig. 1 is marked B; its general principles of action being conventional, but its preferred form being shown in :other figures especially Figs. 3 to 5. The separator means C, D is so marked in Fig. 1 as to its signature edge depressing mechanism C and its stack lifting mechanism D; these being shown more fully and in detail in Figs. '7 to 10. The yextracting drum is well shown in Fig. 1, marked E; and this element appears in other gures, especially Figs. 16 and 17, and see also Figs. 8, 11 and 18. The conveyor mechanism is marked F in Fig. l, showing the trough with its rear and front supporting plates and the endless conveyor chain with its group-thrusting pins; this mech- -an-ism being more fully illustrated, and its driving connections disclosed, in Figs. 20 to 24. Likewise the group jogging mechanism, marked G, is seen in Fig. 1, cooperatively adjacent to the conveying mechanism; and this and its pulsating ydrive being more fully shown in Figs. 20 to 24. Finally, the detecting or calipering mechanism, marked H, is represented in Fig. 1 by certain of the active parts thereof; and this is shown more completely and with details in Figs. 11 to 15 inc'lusive.

Above the bedplate 3i are various heavy main frame pieces and subordinate xed members, giving support to various parts including brackets on which are mounted the various mechanisms of the machine. The total structure, as explained, is on the unit system, each unit having its own bedplate and upright walls and other nxed frame members, so that, as indicated in Figs. 18 and 19, the machine may be set up with four or eight or twelve or more sections. In each unit Ias best seen in Fig. 19 are two or more upright cross walls 32, the supporting top surfaces of which are designated 42. Other u-prights 33 include frame legs, columns and the like. There are also longitudinal frame members, -acting as girders and supports, and extending between and beyond the cross Walls; a main one of these in each unit being a hollow longitudinal frame piece or casting 34 resting atop the cross walls, this by its top surface 34 giving support to various brackets etc. and interiorly carrying the bearings for the shafts of the four extractor drums in each unit. To the rear of the horizontal frame piece 35 are triangular extensions 35 serving as ro-ckshaft 'bear-ings, while above 34 is an upward extension piece 35, centrally located to serve as an underlying supportt other fixed and movable parts.

Among the various longitudinals of the machine is a flat longitudinal member 31 serving as a shelf and extending the length of the unit at a high rear point, whereon operatives may preliminarily store and arrange batches of signatures to be intermittently transferred from such loading shelf into the hoppers A which stand directly in front thereof. The shelf 31 is supported by bent strips 38, while at the rear below the shelf is an enclosing panel 39, seen in Fig. 1, readily removable for access. An important series of Ibrackets 4D is secured atop wall 32 at the front thereof and these brackets serve to give support to a longitudinal continuous front board 4|, in the nature of a working shelf, at which the operative may bring about corrections when errors of operation have caused the stoppage of the machine.

The conveyor comprises a trough or raceway together with the traveling chain and pins protruding upwardly at a midway point thereof as will be later described. The trough is shown as comprising opposite fixed continuous plates, the front plate :i3 being inclined upwardly frontly while the rear plate 46 may be flatwise, the chain running between them. The accumulating signatures, overlying the supporting plates 4S, 45 have their back edges running longitudinally along the trough back wall 45 as a gage, which wall is preferably upright and carries a series of short angle pieces 4-5 whose horizontal portions overlie the signature edges and act as guards preventing displacement, the spaces between angle pieces accommodating the discharge of the signatures from the drum to the supporting plates 43, 44 below. Longitudinally beyond the conveyor and trough may be conventional supports and group advancing means (not shown) conducting the group procession to a binding machine or other destination.

The hopper H is best shown in the front 'view Fig. l, top view Fig. 3 and rear and left elevations Figs. 4 and 5. Attached upon the top surface 34' of the longitudinal frame piece 34 is an upstanding bracket 43, of U-shape, having an upright rea-r extension or leg spaced from the main wall 49, but the two interconnected by the bracket base and an interior bridge l, there being a transverse bore through the parts 49, 55 and 5 l. The main upright wall 45 is formed at its upper part with an elongated longitudinal portion 52, being a xed part of the hopper.

The hopper is of preferably open or skeleton structure throughout. 1t derives support generally from the bracket wall portion 52 and by a hopper base bar 54, extending fore-and-aft or transverse to the longitudinal dimension of the machine. The base bar 54 is secured nxedly in position by having its rear end turned down to t the bore in the bracket 49, this turned end being shown secured in the bracket by a set screw 53. At the front end of the base bar 54 there is fixedly attached to it by an underneath bolt a longitudinal bottom bar 55, which is opposite to the longitudinal extension 52 of the supporting bracket, the floor members extending fore and aft between said xed members 52 and 55. The actual iioor consists of a number of cross members, these preferably being idler rolls or freely rotatable supports carried upon their shafts or spindles which at their ends turn in open bearing slots 57 at the top side of the longitudinal bar 56, and closed slots or bores 58 formed at the same level in the longitudinal portion 52 of the hopper bracket. By this arrangement of rolling supports the extraction of each lowermost signature is considerably eased, the character of the rolls eliminating friction at the underside of the signature being extracted.

Referring further to the rolling skeleton floor, the support of the floor rolls is by the ends of their spindles, turning in the iixed members 52 and 56, excepting that a short bent bracket 60 is used for the rear end of the iinal roll 6|, thus to space the roll end away from the critical corner of the hopper Whereat the suction detaching and the separating actions take place. The semi-final door roll 62 is shown as a plain cylindrical roll, each signature as it is extracted leftwardly out of the hopper rolling upon the last two rolls 62 and 6|. The remaining signature supports may substantially all consist of rolls, and there are next shown three rolls 63, of graduated shapes, each of which is crowned or barrelled at its central part, affording a distinct tendency to arch the central portion of the stack thereby to minimize the pressure of the second and subsequent signatures upon the one which is under extraction. The nal support @Il is necessary initially to hold the trailing edges of the stacked signatures and is shown also as a revoluble element, of similar diameter to the rolls 63 and larger than the diameters of the rolls 6I and 52. The set of six illustrated rolls in each hopper is found to give improved reliability in the extraction of signatures one at a time. The crowned rolls minimize the danger of a second signature being pulled when the i-"irst is being extracted.

Coming to the four hopper skeleton walls, that which is at the lefthand side of the hopper is shown as consisting in an upright metal strip 66, a single such wall element being sufficient, and this constituting a stop, at the exit side, against which the signature leading ends S3 bear when inserted into the hopper. The wall strip 56 is screw-attached to the portion Gl of a iixed bracket, the other portion 58 of which is secured t0 the longitudinal frame wall 34. To the iront side of the bracket 61 is attached an upright angle iron 10, and each member 'it takes part in giving support to the righthand wall of the next hopper, the latter wall consisting of a single upright strip 1l, the lower end of which is screwattached to the angle iron l5.

Coming to the rear wall of the hopper, this is shown as composed of two upright strips 13, and these two strips are attached by screws 'I4 to the elongated top portion 52 of the hopper bracket 49. At the front the hopper is of a special construction consisting of a series of ve upright rods, and these rods as a group are arranged to be adjustable rearwardly for a narrower signature and vice versa. This adjustment is provided in the fact that the lower ends of the wall rods 76 are tted into recesses formed at the upper side of a shiftable longitudinal bar 'il. The size adjustment is effected by sliding the bar 'Il along upon the fixed transverse bar 54, with screw means to secure the desired adjustment. It is suicient to effect adjustment of the front wall by shifting the rod group 16, and adjustment of the righthand wall or upright strip 'il by loosening the angle iron 'i9 and shifting it to a new position on the bracket 6l and securing it again to the bracket.

It .is desirable to supplement the hopper by certain inwardly projecting members, which may be termed ledges, arranged to permit portions of the stack to be hitched up peripherally, above the body of the stack thus, at the stack edges where aesinet these proje'ctions are arranged, acting to relieve materially from the weight and pressure of the stack the lowermost signature, reducing the frictional resistance upon it and facilitating its extraction below the lefthand Wall of the hopper. Thus on the front wall composed of the upright rods 'i5 there maybe a series of ledge members 8i), shown in Fig. 5, these being well above the hopper bottom and therefore adapted only to assume part of the `weight of the upper portion of the stack when it is fairly lled with signatures. At the left wall, consisting of the upright wall strip bb is provided a ledge consisting' of adjustable screws 8| standing inwardly from a fixed supporting plate 82. As seen in Fig. i this device, not far from the signature corner, gives upcurved support to the leading edges Ss of the stacked signatures other than a minor group of them which have escaped from the ledges. Figs. 3 and 4 show also, lat the Wall 6B, a low ledge piece $.13 consisting of a small angle piece with its lower portion projecting inwardly below the lowermost signature level, thus to minimize the possible drooping downwardly of the leading edges of the lower signatures; and a similar ledge piece 83 is attachedat the foot of wall 7|. At the righthand wall of the hopper is shown a third style of ledge consisting of an upright strip fl with an inbent foot 85 upon which may rest in elevated position the trailing ends of the stacked signatures above a certain elevation. In these ways the stack edges, to a material extent, are supported upwardly away from the lower signatures of the stack, relieving considerably lthe frictional pressure upon the lowermost signature, as stated.

It is preferably also to have a small and slightly elevated ledge or step 86, upholding the tips of a lower group of signatures, at the corner of the triangular area S5 whereat the suction detacher means operates; this corner step piece assisting in protecting the signatures, above the bottom signature, from being detached and swung .downwardly from the stack when .the bottom signature is thus manipulated by the sucker device. This corner ledge or step 85 is supported in place upon horizontal leg of a .belt supporting rod 8'.' which in turn upwardly passes through and is secured to a horizontal .bar 'screwi-attached on top of the longitudinal upper portion V52 .of the hopper bracket t9. All .described ledges or edge supports are adjustable according to the kinds and sizes of signatures.

Having described the signature hopper and before describing the suction-detaching andother active mechanisms, the longitudinalmain or cam shaft Se and certain associated elements will be described. This shaft takes its bearings in the frame cross walls 32 and similar cross walls 33 near the ends of the machine. Like other main elements the main shaft is sectional, Awith a continuous shaft portion in each `u-nitof the machine. The ends of the shaft portions in each unit extend freely beyond the bearings, and veach two adjoining shaft sections are tightly connected .by couplings 9 i, as best seenin Fig; 19. The-main shaft carries certain cams and gears as -will be further explained. This shaft may turn clock-wise as seen in the left -view `lig. 1, filiglltl'y above the main shaft, and to the front of it is an axle 193, preferably fixed and ser fingalso as a frame rod; and there are other longitudinal rods Vfor the most part unnecessary to describe. Well above the shaft 9b and axle '93, and l rearward thereof in each unit is a longitudinal rockshaft A95, and

- 10 somewhat thereabove there is a second roekshaft S6; these rockshafts constituting parts of different trains of mechanisms as will be further described. The upper rockshaft S5 takes its bearings in the triangular rear brackets 335 constituting extensions of the heavy longitudinal vframe member Ell, ywhile attached rear brackets 91 give bearing to rockshaft 95. The main shaft may be power driven in any suitable manner, and, being For its drive the main shaft may carry a Igear 98,

Fig. 2l, in mesh with a primary gear 9 9, driven for example from japowerful leill'ctric motor, not shown. The Ygear 99 maybe consideredthe ,source of power for the Ventire machine.

The 'suction detaching means B is `best shown on Figs. 3, 4 and 5, with 4actuating connections shown also in Fig. 1. be considered the sucker 'memben and this VKis provided 'with one 'or preferably tWO lipstanding suction cups IDI, as of elastic rubber, adapted to be brought into vcontact with the lowest vsignature 'at its triangular corner S5 to hold and lower `or detach such corner from the signatures above. The swingabl'e` sucker `head v| 6 6 `is mount'- ed at the end of 'a hollow shank |02 mounted for rotation, and with a .bend or 'eccentric offset |63, like a crank, lbetween the ybearing `and the head so as to swing the'ljatter .up and down when the shank is rotated, the sucker being well within the voutline of the signature :corner during its operative movements. The main portion 'of the shank |62 is straight and extends vthrough a xed bearing |04, in the form of a sleeve or barrel attached byscrews vIt?) to the top Aend of the hopper bracket Vrear wall 5U. The bearing sleeve A|811 and the 'hollow sucker shank therein are arranged in asubstantially'level yposi-- tion, but at a decided diagonal direction, prefer'- ably 45, thus providing a rotation axis |06 which is a continuation 'of the diagonal bend Vline Ss of the signature as already described, so that When the sucker is Yswung up and then down it will bend the signature corner 'downwardly about the imaginary line constituting the sucker axis 'of swinging. The far or right-:rear end of the sucker shank has fitted `to ita flexible tubing |01 extended to a suitable jor conventional suction maintaining apparatus, with controlling valves between, .in order to apply and remove the suction at the proper 4points 'of time to take hold upon [and later to release 'e'a'ch signature in accordance with the cycle of kopera-'- tions which will be hereinbelow detailed. The function of the detacher member l, |'|i`| 'is to contact and stick to the signature .underside so as Vto pull it down, suction being a typical means for' such sticking and pulling.

The remaining mountings .of the suction dye'- tacher device maybe as follows, permitting the rotary or oscillating vmotions ofthe shank .within the bearing sleeve |04. The straight .portion of the shank, between the bearing and the ybend |63 is provided with a collar |69 .which turns against the end of the bearing. vAt the far 'end of the bearing the hollow shank is surrounded by a clamp member lill, and this clamp member may be the hub fof Varockarrn extending laterally and having a swingable'head l| 2V within which is clamped a pivot pin |-|'-3, upon Vwhich in turn is engaged the upper end or `head |123 of a -long drop-link 1||5, Ithese parts being best A hollow head '|80 may' seen in Fig. 3 and in Fig. 1 taken with Fig. 2. At its lower end the link ||5 has a pivotal connection H6 with a radial arm the latter being clamped by its hub ||8 to the rockshaft 95 previously described. By this airangement the rocking of the shaft 05 transmits the to and fro motions through the elements Ill, IIB, ||5 and to cause the sucker shank to oscillate, thereby swinging upwardly and downwardly the sucker or head |00, to perform its signature corner detaching operations in accordance with the cyclical timing hereinbelow described.

The rocking of the shaft 95 through which the actuation of the suction device and connections are effected from the main or cam shaft 90 may be as follows; these connections between the main shaft and the counter-rockshaft serving also for the operation of part of the detecting mechanism H. Starting with the main shaft, this carries a large cam or disk |20 whose hub |2| is secured to the shaft, these parts being best shown in Figs. 1, 18 and 19. The cam |20 has formed within its lefthand side a cam groove |22, of a contour having a rise and a drop between long and short dwells; the contour being shown in Fig. 1 and being determinable also from the cycle of operations yet to be outlined. In the groove |22 runs a follower or roller |24, mounted at the free end of an oscillating cam lever |25, mounted to swing loosely about the fixed axle 93. At a midway point the lever is provided with a pivotal connection through which the lever actuates an upwardly extending link |21, the upper end of which has a pivotal connection |28 with a rockarm |29 secured to the rockshaft 95 by a collar or clamping hub |30. The pivot |28 is of a kind that is adjustable as to the length of the radial arm |29, this being provided through a longitudinal slot in the arm engaged adiustably by a pivot pin at the top of the link |21; thereby permitting the angular throw or oscillation of the rockshaft 95 and the movements of the trains of parts actuated thereby to be adjusted at will.

Coming to the separator mechanism this, as already explained, comprises two separate but closely associated mechanisms, C the signature edge depresser means and D the stack lifting means. lhese parts are best shown in Figs. 7 to 10 taken with the left view Fig. 1 and the actuating connections seen in Figs. 18 and 19. Referring first to Fig. 7 the depresser means comprises a bent nger or blade |35 at the end of the swingable shank |36, while the lifter device comprises a blade |38 at the end of its shank |39. Each of these instruments may be of L-shape as a convenient way of mounting them to swing inwardly, above the detached bottom signature, from the dotted line position seen in Fig. 7 to the full line position, the two blades swinging in unison about a vertical axis represented by the upright shaft |4| from which they take their simultaneous swinging motions. While the two instruments move in and move out in unison, preferably by swinging, the other movements are differentiated, the depresser blade |35 moving downwardly, after it has entered between the lowest signature and the stack, to insure the lowest signature reaching the drum and gripper; the lifter blade at the saine time moving upwardly to apply lifting pressure to the stack to ease the friction on the lowest signature thereby to assist extraction. In each case the down or up movement may, and preferably does, commence during the inward shift or swing, thus to conserve time; and these down and up movements may comprise dwells for refinement of action, as will be explained hereinbelow in summarizing the preferred total cycle of actions. The inswinging shift of the separator blades into the gap is superior to a straightline or sliding entry, reducing vibration and permitting diagonal entry over the signature corner, where the gap is widest.

As the illustrated separating mechanism C, D is organized the same means which shifts the blades inwardly and outwardly serves also to cause the predetermined down and up movements of the blades. Leaving these latter movements for later description, the swinging movements take place about the upright shaft |4|, which is tted to rock through a substantial angle, illustrated by the difference in the full line and dotted line positions in Fig. 7. Specifically when, through shaft |4|, the blades are swung in or out, these motions cooperate with fixed cams to be described, one for the depresser blade and the other for the lifter blade to afford their down and up movements. By this arrangement it is only necessary to provide for the correctly timed rocking movements of the upright shaft |4| in order to deliver all of the described actions to the two mechanisms of the separator means.

The rocking of upright shaft |4| may be brought about through a radial rockarm |42 extending frontwardly and leftwardly as seen in dotted lines in Fig- 7, this arm being swung by means of a long link |43, which only has to be moved frontwardly and rearwardly to cause the complete motions of the mechanism, a pivot |44 connecting |43 with |42. For convenience the actuation of this train of elements |43, |42, |4| will be described in advance of the details of the separator mechanism. The actuating connections to the long fore-and-aft link |43 are best shown in Figs. 1, 18 and 19. On the main cam shaft is a cam disk |45 whose hub |46 is fast on the shaft, near the left end of each section of main shaft. The groove |41 in the face of the cam disk is well shown in Fig. 1 as comprising a rise and a drop of contour between two extended dwells, the cam rise acting upon the follower roll |48 causing the inward movements of the separator blades. A cam lever |50 is fulcrumed on the same rod or axle 93 as the lever |25 already mentioned, the lever |50 having at a middle point a pivot |5| by which the lever is connected with an upwardly extending link |52, the top end of which in turn is pivoted at |53 to a rockarm |54 whose hub |55 is clamped fast upon the rockshaft 96 already mentioned. At another` point upon this rockshaft is an upwardly extending rockarm |56 secured by clamp |51 to the rockshaft. By this arrangement the motions derived from the cam |45 are communicated as fore-and-aft swinging movements of the upstanding lever |56 which in turn is connected by a pivot |58 to the rear end of the long horizontal link |43 already mentioned.

The general bracket 36, serving both for the separator means and part of the detector means, is formed with an upper front extension |60 upon the top of which is mounted an irregular separator bracket |5|, as seen in Fig. l and Figs. 7 to 10, this bracket having a tubular upright extension or bearing |62 for the upright axle or rockshaft |4|, already mentioned, one of the transmitting parts of the separator mechanism. At its upper part the bracket |6| has a rightward extension which provides a tubular boss or socket |63 'within which is fixed a depending post or rod |54 for the support, at its lower end, of certain parts of the mechanism, a bolt |65 extending upwardly from below and being threaded into the lower end of the post to hold such other parts between the bolt head and post end.

As already stated, the adjacent biades |35 and |33 have to shift in and out horizontally in unison while at the same time moving up and down f oppositely, during the separating actions. For mounting the iades to receive their movements the following is an example. The depresser blade 35 has its shank |36 extend-ed at |35', the left leX- tremity of which is for-med into a hub |31, which turns upon a horizontal pivot pin |61, best Aseen in Figs. 9 and i9 thereby permitting the depresser to swing down and up. Likewise the shank |39 of the lifter bla-de has an extension |39', the left end of which is formed into a hub lil!) surrounding the pin il'; but instead of swinging up and down it is preferred and simpler to elevate and lower the lifter in a bodily movement with the rockshait itil. By this mounting of the blades they are independently movable upwardly and downwardly, while compelled to shift or swing horizontally inwardly and outwardly in unison. The upward and downward movements of the blades are effected by a low fixed cam for the depresser blade and a high fixed cam for the lifter blade, so that sai-d movements are brought about by reason of the inward and outward swingings of the blades, and are timed by the contours or said cams.

The upright rockshaft lili has been described in regard to the means for rocking or oscillating it, through its arm ist?, the long link |43 etc.; and when it rocks the shaft swings the two blades as described. The shaft mi also has a limited vertical movement, as shown by the spaces at the ends of the shaft bearing H32, this vertical play being caused by the overhead fixed cam to be described and serving to lift and lower the stack lifter blade. This motion is communicated also, to the hub |31 of the depresser blade, unnecessarily but negligibly. The shaft I4! is shown as provided at its low end with a collar |69, which may also be the hub of the rock-arm |42, and this collar at its lower portion is forked to provide two depending legs, a front leg |10 and a wider rear leg I'H, with a substantial space between them accornmodating the hub |31 of the depresser blade shank, the pivot pin |61 having its ends mounted in the two legs of the fork or yoke |69. The hub i of the lifter shank is integral or rigid with the rear leg |1| of the yoke of shaft collar ili, so that the lifter is rigid with the shaft lill and rises and lowers as well as swings in and out with it.

The fixed cam means for controlling the up and down movements of the depresser and lifter blades is illustratively shown as follows. On the shank |36 of the depresser bla-de is mounted a cam roller |13, which rolls around an arc concentric with the upright rockshaft Ml. The roller plays between an upper cam track or race |111 of the same concentric shape and a corresponding lower cam track member |15. These cam parts have complementary contours facing each other and between which the roller travels, thus to deliver down and up motions to the depresser blade. At their front ends the cam tracks or strips are threaded on to the bolt H55, which ispassed upwardly through an aperture in the lower track and thence through a spacing sleeve |16 and 14 Y thence through the aperture in the upper track, so that when the bolt is tightened these parts are iirmly held in position. lThe other or rear ends of the cam tracks |1-'i and |15 may be fixed in position by means of a face plate |11 to which the cam ends are secured and which in turn is secured to the general bracket 36. The contour of the cam path, between its upper and lower tracks is preferably a simple contour with .a -single incline between two dwells, as best shown in Fig. 9.

Similarly the up and down movements of the lifter, attached rigid-ly to one leg of the yoke .ISS at the foot of the rockshaft l I, may .be performed as follows. nt the top of the rockshaft is secured by a hub clamp id@ a radial .arni Siti carrying a roller i552 adapted to roll alo-ng .between upper and lower fixed cam 'tracks lll and It. The lower track is shown mounted upon the top surface 16| of the separator .bracket it l. Bymeans of tubular vspacers 18e 4the .upper track |33 is properly spaced above the lower track, and `these are :all held rigidly in position by means of headed bolts .|31 passed downwardly through apertures in the two tracks and through the spacers into threaded bores in the bracket.

The shaping oi the fixed cams aiiords a timing of the up anddown movements of both blades a manner coordinated with the general cycle to be described; but at this point yitmay be mentioned that in a preferred embodiment the total swing of the two separator blades is-about 56, measured around the axis of the upright `rockshaft 55E-i. During the-Erst vpart-of eachinswinging movement, when the blades wedge their way in between the detached signature `below and the stack above, the depresser blade enters the space with a level movement, whichcontinues for 40 of angle, and then dips or swings down for' the iinal 16", depressing the signature leading edge linto the reach of the drumgrippers. The lifter blade may have a somewhat different movement, swinging-inward at a vlowlevel for about 8, making sure of clearing .theundersidefof the remaining stack, then risingslightly intorinitial contact with the stack,and only undergoingthe remainder of'its rise during thenal 16- of swing, thus to give upward pressure againstthe stack about the time the extraction of the signature begins; and the total up and lown movementof the lifter blade vmay be ofthe order of 1/4 inch. In respect to insuring the safe entrance of the two blades into the space between stack and signature the described swinging arrangement is of substantial advantage, affcrding a swinging motion under which the noses of the blades enter the space quite near-to the corner of the stack,lat whichthe space is maximum, aording maximum clearance ior the inswing of the blades.

Theextractor mechanism E comprises-'a generally conventional drum of the open or. skeleton type, with grippers adapted togrip eachlowest signature in the hopper for extraction, transfer and discharge to the conveyor, the drum operating on known principles but yof improved structure. It rotates about a transverse axis incounterclockwise direction, looking from thefront, so that the extraction ofeach signaturefis generally leftwise, the opposite-to the-rightwise traveloi the conveyor below, using the principle of multiple gripper sets, two such sets'are mounted oppositelyon -the drum, whichv therefore irrits drive is geared down to-rotate at half the speed of the main shaft. The drumY is best lshown inrFigsl, 16 and 17, with further illustration of its drive in Figs. 18 and 19. Surrounding the drum shaft, but freely rotatable by reason of a ball bearing 35| as will be described, is shown a member 350 of the calipering mechanism, adjacently to the rear of the drum as will be further described.

The illustrated open drum structure, for each section of the gathering machine is shown as comprising a pair of circular side disks |89 at the front side and |90 at the rear side, with an interrupted cross web |9| interconnecting them about midway between the periphery and center of the drum. Interiorly arranged, as a separate casting is a circular or hub member having an outstanding ange |92 which is attached by bolts |93 to the inner side of the rear drum disk |90; and said circular casting has also a cylindrical flange |94 extending rearwardly where it is firmly connected by a key |95 to the rearwardly extending drum shaft |96.

The bearing for the rotary shaft |96 comprises a cylindrical cast piece or sleeve |98, surrounding the shaft, with one or more bushings |99 interposed. The bearing sleeve is formed with an outstanding flange 200 which is bolted against the rear side of the hollow longitudinal frame casting 34. By way of spacing the drum correctly frontwards of the hollow frame piece 34 there are shown certain spacing members between the frame piece and drum. One of these comprises a hub 202 immediately surrounding the bearing piece |98 in front of the frame piece, this conveniently being the hub of a stationary but adjustable gripper operating cam or disk 203 formed with a cam groove 204 at its front side cooperative with the gripper connections yet to be described. Other spacing elements are indicated in Figs. 1 and 16 substantially filling the space between the drum and the frame casting 34. For adjusting the fixed position of the gripper cam 203, thereby to give accurate timing of the gripper closing actions, there is shown in Fig. 17 a radial extension 205, which is concentrically elongated and formed with a slot 206, within which slot are located opposite adjusting screws 201 bearing upon a central stud 208 outstanding from the frame wall 34. By loosening one of the screws 201 and taking up the other, the angular position of the cam member 203 may be set as desired, and the adjustment fixed by means of lock nuts 209 near the outer ends of the adjustu ing screws.

Before describing the gripper mechanism, for convenience, will be described the preferred mode of drive of the drum shafts, in unison, remembering that there are four such drums and shafts in each longitudinal unit of the machine. A common mode of drive of multiple drums has been by the use of bevel gears, but this has proven unsatisfactory in several respects and the following disclosure is found to improve the accuracy and efficiency of drive. This mechanism is shown on Figs. 18 and 19, the latter being in rear view, the former showing the drum shafts and one of the drums, in top view. Each drum shaft extends through the longitudinal casting 34, as already described, with its ends projecting rearwardly therebeyond. The plan disclosed is a particular use of sprocket gearing; each pair of the two pairs of drum shafts in each unit being thus geared together, this arrangement being supplemented by power drive through a third sprocket gear train operating upon one of the two drum shafts of each of said pairs. Thus, at the rear end of each drum shaft, mounted thereon by a hub 2|| is a sprocket wheel 2|2. In each pair,

taking the pair appearing at the left end of Figs. 18 and 19, there is a single interconnecting sprocket chain 2|3, this chain passing around both of the sprockets and being held taut by an idler take-up sprocket wheel 2|4 which is mounted at the free end of a swinging arm 2|5 whose hub 2|6 is loose upon the drum shaft, and pressed by a spring 2 to thrust the chain into the space between the two wheels, thus insuring tight coordination between the two wheels, as well as a more extended engagement of the chain with the wheels. On account of the d irection of the common drive of the two chains 2|3, to be described, the take-up idler 2|4 of the lefthand sprocket train in Figs. 18 and 19 is arranged to press upwardly on the lower stretch of chain, whereas at the righthand end the idler is pressed downwardly upon the upper stretch of chain2l3.

For a common drive for the two pairs of sprocket wheels 2|2 the following arrangement is preferred. By their hubs 2|9, keyed to the middle two of the four drum shafts |95 auxiliary or secondary sprocket wheels 220 are provided, of equal size t0 the sprockets 2|2; `and a driving sprocket chain 22| is arranged to pass around the two secondary sprocket wheels 2|9, and thence downwardly to the driving point. The driving train for the four drum shafts of each unit commences with the main or cam shaft 9S, upon which is xed a spur gear 223 which is in mesh with a spur gear 224, these having unitary ratio, the gear 224 being mounted upon the input shaft 225 of a centrally located gear box 22E attached upon the bed plate 3|. The gear box contains conventional means for communicating drive at right angles, so that the output shaft 22'! stands fore-and-aft or transversely of the longitudinal direction of the main shaft. Upon the shaft 221, which makes one rotation per cycle, is mounted a sprocket wheel 223, around which the chain 22| passes. This chain therefore travels around a substantially triangular path, communicating the drive to the two auxiliary sprocket wheels 220, and thence to the middle two of the four drum shafts and, through the main sprocket wheels 212 to the remaining two drum shafts. To prevent loose play in the triangularly disposed sprocket chain 22| there is provided an idler take-up sprocket wheel 229, which is adjustably mounted upon a bracket 230 secured upon the central gear box 226. Thus the four drums and their shafts in each unit of the machine are driven from and in coordination with the main shaft and the other mechanisms that are driven by the latter. The extracting drums E being of the kind with two gripper sets it is necessary that the rotary speed of the drum shafts should be but half of that of the main shaft, and this is provided in the disclosed mechanism by the fact that the sprocket wheel 228 on the output shaft of the gear box is of one-half the diameter and onehalf the number of teeth of the drum shaft sprocket wheels 220 and 2 2.

Returning to the drum and its two gripper sets, Figs. l, 16 and 17, each gripper comprises its swingable jaw 232 cooperating with a fixed abutment 236, the jaw being shown open at the upper side of Fig. 17 and closed at the lower side. There is shown a means for adjusting the pressure of each gripper when closed against the abutment, this consisting in a back finger 233, outwards of the jaw 232, the linger being heavier and stiffer, and provided with a headed screw 

